Strut mount bearing unit

ABSTRACT

A strut mount and bearing assembly includes a strut mount having upper and lower ends, a central bore for receiving a shock absorber end and an annular upper race surface between the upper and lower ends and extending circumferentially about the bore. The upper end is fixedly connectable with a vehicle body and has a flat attachment surface disposeable against a vehicle surface of the vehicle body. A first bearing race is disposed on the mount and a spring seat having a second bearing race is movably coupled with the strut mount. The seat also has a lower end with spring engagement surface and a second bearing race is disposed on the seat spaced axially from the first bearing race. Rolling elements are disposed between the first and second bearing races to form a bearing. The various components are formed and sized to make an axially compact assembly.

BACKGROUND OF THE INVENTION

The present invention relates to vehicle strut assemblies, in particularto strut mounts including bearings.

Strut mount assemblies are known and are used to connect a vehicle strutwith a vehicle frame or body. A typical strut assembly, for example aMcPherson strut assembly, includes a strut mount attached to the vehicleframe or body and a shock absorber disposed within a tubular housingconnected to a steering knuckle of the wheel hub and having a shaftattached to the strut mount. A coil spring extends between the tubularhousing and an upper spring seat and a bearing assembly is disposedbetween and rotatably connects the upper spring seat with the strutmount. Generally, the separate bearing assembly and the spring seat areassembled onto the strut mount with no retention means or with a lightpress-fit of the bearing assembly inside of the strut mount. In certainapplications, the centerline of the load applied by the spring upper end(i.e., onto the spring seat) is angled with respect to the centerline ofthe shock absorber, which either causes transverse loading on thebearing or necessitates orienting certain components to align thebearing with the spring, which typically increases the amount of spacerequired between the vehicle frame and the steering knuckle.

SUMMARY OF THE INVENTION

In one aspect, the present invention is a strut mount and bearingassembly is provided for connecting a wheel strut unit with a vehiclebody, the strut unit including a shock absorber with a shaft extendingalong a central axis and a suspension spring having a load centerline.The assembly comprises a strut mount having upper and lower ends, acentral bore extending generally between the upper and lower ends and agenerally annular upper race surface disposed between the upper andlower ends and extending circumferentially about the bore. The upper endis configured to fixedly connect with the vehicle body and has agenerally flat attachment surface extending substantiallyperpendicularly to the centerline and disposeable against a surface ofthe vehicle body. The strut mount central bore is configured to receivean upper end of the shock absorber shaft and has a centerline extendinggenerally collinearly with the shock absorber axis. A generally annular,first bearing race is disposed on or provided by the upper race surfaceof the strut mount and has a central axis, the bearing race axis beinggenerally coaxial or parallel with the spring centerline. A spring seatis movably coupled with the strut mount and has an upper end with agenerally annular lower race surface and a lower end with a generallycircular engagement surface. The engagement surface is contactable by anupper end of the suspension spring and has a center and a diameter.Further, a generally annular, second bearing race is disposed on orprovided by the lower race surface of the spring seat and is arrangedfacing generally toward and spaced axially from the first bearing race.Also, a plurality of rolling elements disposed between the first andsecond bearing races so as to form a bearing. Furthermore, the strutmount and the spring seat are each sized and configured such that aratio of the diameter of the spring engagement surface to an axialdistance between the upper attachment surface and the engagement surfacecenter is greater than three.

In another aspect, the present invention is again a strut mount andbearing assembly for a wheel strut unit, the strut unit including ashock absorber with a shaft extending along a central axis, a suspensionspring having a centerline angled with respect to the shaft axis. Theassembly comprises a strut mount including a hub with a central bore forreceiving an upper end of the shock absorber shaft, the bore having acenterline extending generally collinear with the shock absorber axis,and a generally cylindrical mount body with an upper end configured tofixedly connect with a vehicle body and a lower end. A generallycylindrical, elastomeric damper member is disposed generally coaxiallybetween and connects the hub with the mount body. A generally circular,first bearing race is attached to the lower end of the strut mount so asto extend circumferentially about the damper member and having a centralaxis. The bearing axis is generally coaxial or parallel with the springcenterline. A spring seat is movably coupled with the strut mount so asto be angularly displaceable about the bearing axis and has an upper endand a lower end with a generally circular support surface contactable byan upper end of the suspension spring. A generally circular, secondbearing race is attached to the upper end of the spring seat so as to befacing generally toward and spaced axially from the first bearing raceand extending circumferentially about the damper member. Further, aplurality of rolling elements are disposed between the first and secondbearing races so as to form a bearing.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

The foregoing summary, as well as the detailed description of thepreferred embodiments of the present invention, will be betterunderstood when read in conjunction with the appended drawings. For thepurpose of illustrating the invention, there is shown in the drawings,which are diagrammatic, embodiments that are presently preferred. Itshould be understood, however, that the present invention is not limitedto the precise arrangements and instrumentalities shown. In thedrawings:

FIG. 1 is an exploded view of a first preferred construction of a strutmount and bearing assembly, shown with the bearing axis aligned with thecenterline of the spring upper end load;

FIG. 2 is a cross-sectional view of the first construction strut mountassembly, taken along the shock absorber central axis;

FIG. 3 is another view of the strut mount and bearing assembly of FIG.2, shown without the suspension spring, shock absorber shaft and bumper;

FIG. 4 is an enlarged view of a section of FIG. 3;

FIG. 5 is another view of the strut mount and bearing assembly of FIG.2, indicating the spring seat engagement surface diameter, bearing pitchdiameter and axial spacing of each from the strut mount attachmentsurface;

FIG. 6 is a top perspective view of the first construction strut mountand bearing assembly;

FIG. 7 is a bottom perspective view of the first construction strutmount and bearing assembly;

FIG. 8 is a side plan view of a strut mount of the first constructionassembly;

FIG. 9 is top perspective view of the strut mount of FIG. 8;

FIG. 10 is bottom perspective view of the strut mount of FIG. 8;

FIG. 11 is an axial cross-sectional view of the strut mount body of FIG.8;

FIG. 12 is a side plan view of a spring seat of the first constructionstrut mount and bearing assembly;

FIG. 13 is an axial cross-sectional view of the spring seat of FIG. 12;

FIG. 14 is an axial cross-sectional view of an alternative constructionof the strut mount and bearing assembly, having an upper bearing racediametrically larger than a lower bearing race, and including a steelspring seat surface;

FIG. 15 is another view of the strut mount and bearing assembly of FIG.14, showing the suspension spring, shock absorber shaft and bumper andindicating the spring seat engagement surface diameter, bearing pitchdiameter and axial spacing of each from the strut mount attachmentsurface;

FIG. 16 is an axial cross-sectional view of a further alternativeconstruction of the strut mount and bearing assembly, having a bearingaxis aligned with the shock absorber axis;

FIG. 17 is another axial cross-sectional view of the strut mount andbeing assembly construction of FIG. 16, shown without the suspensionspring, shock absorber shaft and bumper;

FIG. 18 is another view of the strut mount and bearing assembly of FIG.16, indicating the spring seat engagement surface diameter, bearingpitch diameter and axial spacing of each from the strut mount attachmentsurface;

FIG. 19 is a top perspective view of the strut mount and bearingassembly construction of FIG. 16;

FIG. 20 is a bottom perspective view of the strut mount and bearingassembly construction of FIG. 16;

FIG. 21 is an axial cross-sectional view of the strut mount and bearingassembly construction of FIGS. 16-19, shown with an alternativeone-piece spring seat;

FIG. 22 is an axial cross-sectional view of a yet another alternativeconstruction of the strut mount and bearing assembly, having a bearingaxis aligned with the shock absorber axis and a shock bumper engagedwith the strut mount body;

FIG. 23 is another axial cross-sectional view of the strut mount andbeing assembly construction of FIG. 22, shown without the suspensionspring, shock absorber shaft and bumper;

FIG. 24 is another view of the strut mount and bearing assembly of FIG.22, indicating the spring seat engagement surface diameter, bearingpitch diameter and axial spacing of each from the strut mount attachmentsurface;

FIG. 25 is an axial cross-sectional view of an even further alternativeconstruction of the strut mount and bearing assembly, having a bearingaxis aligned with the shock absorber axis and a shock bumper engagedwith the spring seat; and

FIG. 26 is another axial cross-sectional view of the strut mount andbeing assembly construction of FIG. 25, shown without the suspensionspring, shock absorber shaft and bumper.

FIG. 27 is another view of the strut mount and bearing assembly of FIG.25, indicating the spring seat engagement surface diameter, bearingpitch diameter and axial spacing of each from the strut mount attachmentsurface;

FIG. 28 is an axial cross-sectional view of yet an even furtheralternative construction of the strut mount and bearing assembly, havinga bearing axis aligned with the shock absorber axis and a spring axisinclined with respect to the bearing axis; and

FIG. 29 is another view of the strut mount and bearing assembly of FIG.28, indicating the spring seat engagement surface diameter, bearingpitch diameter and axial spacing of each from the strut mount attachmentsurface.

DETAILED DESCRIPTION OF THE INVENTION

Certain terminology is used in the following description for convenienceonly and is not limiting. The words “lower” and “upper” designatedirections in the drawings to which reference is made and the words“inner”, “inwardly” and “outer”, “outwardly” refer to directions towardand away from, respectively, a designated centerline or a geometriccenter of an element being described, the particular meaning beingreadily apparent from the context of the description. Further, as usedherein, the words “connected” and “coupled” are each intended to includedirect connections between two members without any other membersinterposed therebetween and indirect connections between members inwhich one or more other members are interposed therebetween. Theterminology includes the words specifically mentioned above, derivativesthereof, and words of similar import.

Referring now to the drawings in detail, wherein like numbers are usedto indicate like elements throughout, there is shown in FIGS. 1-29several alternative structures or constructions of a strut mount andbearing assembly 10 for a wheel strut unit 1. The strut unit 1 includesa shock absorber 2 with a shaft 3 extending along a central axis A_(S)and a suspension spring 4 having an upper end load centerline L_(S)(i.e., the line of force F as applied by the spring upper end 4 a ontothe spring seat 16 (described below)), either coaxial or parallel with,or angled with respect to, the shaft axis A_(S). The strut unit 1 alsoincludes a tubular member (not shown) disposed about the shock absorber2 and supporting a lower end (not shown) of the spring 4 and a bumper 5for transmitting axial loading from the shock absorber 2 to the strutmount assembly 10. The strut mount and bearing assembly 10 basicallycomprises a strut mount 12, a first, upper bearing race 14 disposed onor provided by the strut mount 12, a spring seat 16, a second, lowerbearing race 18 disposed on or provided by the spring seat 16, and aplurality of rolling elements 20 disposed between, and rollablesimultaneously upon, the first and second bearing races 14, 18 to form abearing 11 with a pitch diameter D_(B).

More specifically, the strut mount 12 has an upper end 12 a, a lower end12 b, a central bore 13 extending between the upper end lower ends 12 a,12 b and having a centerline L_(B) extending generally collinearly withthe shock absorber axis A_(S), and a generally annular race surface 24disposed between the upper and lower ends 12 a, 12 b. The strut mountupper end 12 a is configured to fixedly connect with a vehicle body 6(FIG. 2) and has a generally flat attachment surface 15 extendingsubstantially perpendicular to the bore centerline L_(B) and disposeableagainst a surface 6 a of the vehicle body 6. Preferably, the strut mount12 includes an integrated body 22 including a generally cylindricalcentral section 23 providing the strut mount lower end 12 b and agenerally annular flange section 25 extending radially outwardly fromthe central section 23 and providing the strut mount upper end 12 a andthe upper attachment surface 15. With this structure, the upper racesurface 24 is formed on the cylindrical section 23 and has at least aportion, and in some constructions the entire surface 24, locatedgenerally adjacent to the flange section 25. Further, the strut mountbore 13 is configured to receive an upper end 3 a of the shock absorbershaft 3 and has a centerline L_(B) extending generally collinearly withthe shock absorber axis A_(S).

The first bearing race 14 is generally annular, is disposed on orprovided by the upper race surface 24 of the strut mount 12 and has acentral axis A_(B), which is preferably generally coaxial or parallelwith the spring centerline L_(S) (FIGS. 1-27) but may be skewed withrespect to the spring centerline (FIGS. 28 and 29), as described below.More specifically, in certain, “angled” constructions as depicted inFIGS. 1-15, the first race 14 is arranged on the strut mount 12 suchthat the bearing central axis A_(B) is generally collinear or parallelwith an “offset” spring load centerline L_(S) (i.e., the centerlineL_(S) of the spring load or force F (FIG. 2) applied to the seat 16 isangled with respect to shock absorber axis A_(S)) and is skewed withrespect to the bore centerline L_(B) so as to define an angle θ_(B) witha value greater than zero degrees (i.e., the bearing axis A_(B) and borecenterline L_(B) are not parallel). In other, “symmetrical”constructions, as depicted in FIGS. 14-22, the first bearing race 14 isarranged on the strut mount 12 such that the bearing axis A_(B) isgenerally collinear with the strut mount bore centerline L_(B), and thusalso the shock absorber axis A_(S), or generally parallel to the shockaxis A_(S) with an offset in a “radial” direction (not depicted).

In all constructions disclosed herein, the spring seat 16 is movablycoupled with the strut mount 12 so as to be angularly displaceable aboutthe bearing axis A_(B). The spring seat 16 has an upper end 16 a with agenerally annular, lower race surface 26 and a lower end 16 b with agenerally circular engagement surface 17. The spring engagement surface17 is contactable by an upper end 4 a of the suspension spring 4 and hasa center C_(C) and a diameter D_(C). Further, the second bearing race 18is generally annular, is disposed on or provided by the lower racesurface 26 of the spring seat 16 and is arranged facing generally towardand spaced axially from the first bearing race 14.

Referring to FIGS. 5, 15, 18, 21, 24, 27 and 29, in each of the variousconstructions of the strut mount and bearing assembly 10, the strutmount 12 and the spring seat 16 are each sized and configured (i.e.,formed and constructed as described herein and as depicted in thedrawings) such that a ratio R₁ of the diameter D_(S) of the springengagement surface 17 to an axial spacing distance d_(AS), the “springaxial distance”, between the upper attachment surface 15 and theengagement surface center C_(C) is greater than two (2); i.e.,R₁=D_(S)/d_(AS)>2, more preferably greater than 3 and most preferablybetween 3.1 and 5.7. Further, the first race surface 24 is formed on thestrut mount 12 such that a ratio R₂ of the bearing pitch diameter D_(B)to an axial spacing distance d_(AB), the “bearing axial distance”,between the center of the pitch diameter C_(B) and the strut mountattachment surface 15 is greater than three (3); i.e.,R₂=D_(B)/d_(AB)>3, more preferably greater than 5 and most preferablybetween 5.5 and 11.1. Both of these relationships or ratios R₁, R₂provide an indication of the “axial compactness” of the strut mount andbearing assembly 10 and are desired to have the stated values so as tomaximize available space for the shock absorber 2 and the spring 4.

To provide context for the-above structural relationships, a typicalbearing pitch diameter for an automotive wheel hub assembly may rangebetween 60 mm and 130 mm. For sake of illustration, assuming a bearingpitch diameter D_(B) of 100 mm for each of the various constructionsyields the following dimensions and ratios. In a first strut mount andbearing construction of FIGS. 1-13, the spring contact diameter D_(S) isabout 106 mm, the spring axial distance d_(AS) is about 27 mm and theratio R₁ is about 3.9, while the bearing axial distance d_(AB) is about18 mm, such that the second ratio R₂ is about 5.5, as indicated in FIG.5. In a second construction of FIGS. 14-15, the spring contact diameterD_(S) is about 100 mm, the spring axial distance d_(AS) is about 25 mmand the ratio R₁ is about 4, while the bearing axial distance d_(AB) isabout 14 mm and the second ratio R₂ is about 7.1, as indicated in FIG.15. Further, with a third strut mount assembly construction of FIGS.16-20, the spring contact diameter D_(S) is about 108 mm, the springaxial distance d_(AS) is about 23 mm and the ratio R₁ is about 4.7,while the bearing axial distance d_(AB) is about 11 mm and the secondratio R₂ is about 10.1, as shown in FIG. 18. Also, in the modifiedversion of the third construction formed with a one-piece spring seat,as discussed below, the spring axial distance reduces from 23 mm to 19mm, such that the first ratio R₁ is about 5.7.

Furthermore, in the fourth construction of FIGS. 22-24, the springcontact diameter D_(S) is about 129 mm, the spring axial distance d_(AS)is about 24 mm and the first ratio R₁ is about 5.4, while the bearingaxial distance d_(AB) is about 14 mm and the second ratio R₂ is about7.1, as indicated in FIG. 24. Additionally, in a fifth constructionshown in FIGS. 25-27, the spring contact diameter D_(S) is about 102 mm,the spring axial distance d_(AS) is about 33 mm and the first ratio R₁is about 3.1, while the bearing axial distance d_(AB) is about 13 mm andthe second ratio R₂ is about 7.7, as depicted in FIG. 27. Finally, in afifth construction shown in FIGS. 28 and 29, the spring contact diameterD_(S) is about 116 mm, the spring axial distance d_(AS) is about 21 mmand the first ratio R₁ is about 5.5, while the bearing axial distanced_(AB) is about 9 mm and the second ratio R₂ is about 11.1, as shown inFIG. 29. Thus, with the presently preferred constructions disclosedherein, the “spring spacing” ratio R₁ preferably has a value between 3.1and 5.7 and the “bearing spacing” ratio R₂ preferably has a valuebetween 5.5 and 10.1.

Referring now to FIGS. 2-5 and 14-29, the two bearing races 14, 18 arepreferably relatively sized such that one bearing race 14 or 18 has anoutside diameter larger than that of the other bearing race 18, 14,respectively. As such, the larger race 14 or 18 is disposedcircumferentially about the other bearing race 18, 14 in order toprovide radial and axial load support. Specifically, in theconstructions depicted in FIGS. 1-13 and 16-29, the second bearing race18 is sized diametrically larger than the first bearing race 14, suchthat the second race 18 has an outside diameter D₂ larger than theoutside diameter D₁ of the first bearing race 14 and is disposed atleast partially circumferentially about the first bearing race 12, asindicated in FIG. 4. In other constructions, as shown for example inFIGS. 14 and 15, the first bearing race 14 is sized diametrically largerthan the second bearing race 18, such that the first race 14 has anoutside diameter D₁ larger than the outside diameter D₂ of the secondbearing race 18 and is disposed at least partially circumferentiallyabout the second bearing race 18, as indicated in FIG. 14.Alternatively, the two bearing races 14, 18 may be substantially equallysized and configured to provide an axial thrust bearing (not depicted).

Further, the rolling elements 20 are preferably formed as balls andprovide a ball set 20S and the two bearing races 14, 18 preferablyextend both radially and axially so as to form an angular contactbearing assembly 11, as described below. However, the rolling elements20 may instead be formed as cylinders, needles or any other known typeof rolling element and/or the races 14, 18 may be formed as an axial“thrust” contact bearing assembly. Alternatively, the strut mountassembly 10 may be formed without any rolling elements, such that thefirst and second races 14, 18 are formed and engaged in the manner of aplain bearing.

Referring specifically to FIG. 4, each bearing race 14, 18 preferablyincludes a generally annular plate 19 with generally S-shaped axialcross-sections providing a concave raceway surface 19 a and including aradially-extending portion 19 b and an axially-extending portion 19 c.As such, the bearing races 14, 18 are configured to support both radialand axial loading, in combination with support of the strut mount 12 andthe spring seat 16, and most preferably form an angular contact bearingassembly, as discussed in further detail below. Further, each bearingplate 19 is preferably formed of a metallic material, such as low carbonsteel, but may be formed of any other appropriate material.Alternatively, the first bearing race 14 may be provided by the upperrace surface 24, and is thus formed directly on the strut mount 12, andthe second bearing race 18 may be provided by the lower race surface 26,and is therefore formed directly on the spring seat 16. Specifically,the two races 14, 16 may be machined or otherwise provided on each part12, 16, particularly if the mount 12 and seat 16 are formed of ametallic material.

Referring to FIGS. 1-15, with strut mount and bearing assemblies 10 inwhich it is desired to align the bearing axis A_(B) with an offsetspring load centerline L_(S), the cylindrical central section 23 of thestrut mount body 22 is preferably generally wedge-shaped and has agenerally circular, angled race surface 24 located proximal to the strutmount lower end 12 b and extending circumferentially about the firstbearing race axis A_(B) so as to be generally centered on the axisA_(B). The angled support surface 24 is formed on the strut mount body22 so as to have a most proximal axial position P_(P) with respect tothe strut mount upper end 12 a and a most distal axial position P_(D)with respect to the strut mount upper end 12 a, the two positions P_(P),P_(D) being spaced about one hundred eighty degrees (180°) apart, asindicated in FIG. 10. The first bearing race 14 is disposed on the strutmount support surface 24, which positions the circular race 14 in anangled orientation with respect to the bore centerline L_(B), so to beat least generally centered about the spring centerline L_(S).Preferably, the most proximal axial position P_(P) is located at anaxial distance d_(s) of less than one inch (1″) from the vehicleattachment surface 15 on the strut mount upper end 12 a, so as tominimize the axial space requirement of the strut mount and bearingassembly 10, for reasons discussed below.

Alternatively, as shown in FIGS. 14-22, with strut mount assemblies 10having the bearing axis A_(B) aligned with the shock absorber axisA_(S), the central cylindrical section 23 of the strut mount body 12 ispreferably substantially circular cylindrical the upper race surface isgenerally circular and extends circumferentially and substantiallycoaxially about the bore centerline L_(B), and thus about the shockabsorber axis A_(S). As such, the upper race surface 24 is formed on thestrut mount body 22 so as to be at least generally equidistant from themount upper end 12 a at all points about the circumference of the racesurface 24. With such a race surface 24, the bearing first race 14 ispositioned substantially coaxially with the shock absorber axis A_(S).Clearly, such a strut mount structure minimizes the overall axial lengthor height D_(AO) of the strut mount 12, as discussed in further detailbelow.

In certain constructions of the strut mount and bearing assembly 10, asdepicted in FIGS. 1-18, the strut mount cylindrical body 22 is formedsuch that the generally circular vehicle attachment surface 15 extendsacross the entire strut mount upper end 12 a. As discussed above, thestrut mount 12 is preferably disposed against a generally flat/planarbody surface of the vehicle body 6 and connected with the body by aplurality of fasteners 21. In other structures depicted in FIGS. 22-27,the strut mount body 22 further includes an inner, axially-extendingcircular shoulder 27 extending upwardly from a remainder of the bodyupper end 23 a, which is disposable within a circular pocket or recess(not shown) of the vehicle body 7 to assist in positioning the strutmount and bearing assembly 10 on the vehicle.

Referring now to FIGS. 2-4, 13-15 and 18-22, in all of the variousconstructions of the assembly 10, the strut mount body 22 has an innercircumferential surface 29 defining a body bore 31 and the strut mount12 further includes a hub 28 disposed within the cylindrical body bore31 (as best shown in FIG. 10) and a generally circular cylindricaldamper 30 disposed generally coaxially between and connecting the hub 28with the strut mount body 22. The hub 28 provides the strut mountcentral bore 13 and is configured to connect with the shock absorbershaft upper end 3 a, as described in further detail below. Further, thestrut mount body 22 is preferably formed such that the first and secondbearing races 14, 18 extend circumferentially about the coaxiallyarranged hub 28 and damper 30, which enables a reduction in the overallaxial length/height D_(AO) of the strut mount assembly 10, as discussedin further detail below.

Preferably, the strut mount body 22 is formed of a first material, suchas a rigid polymer (with or without a metallic insert to “rigidify” thebody 22) or metallic material (e.g., aluminum) and the damper 30 isformed a second material, such as natural or synthetic rubber. Thesecond, damper material has a substantially greater elasticity than thefirst, cylindrical body material such that the damper 30 is configuredto reduce vibration within the strut mount 12, and thus the vehiclechassis (not shown) and the strut (and thereby the wheel (not shown)).Further, the damper 30 has an inside diameter ID_(D), the hub 28 has anoutside diameter OD_(H) and the damper 30 and hub 28 are preferablysized such that the hub outside diameter OD_(H) is larger than thedamper inside diameter ID_(D), as indicated in FIG. 4. As such, thedamper 30 is thereby compressed between the hub 28 and the strut mountbody 22, so as to provide a preload that optimizes the life of therubber damper 30 by working only in compression and not in tension.

Referring to FIGS. 1-5, 14-18 and 21, in certain constructions of thestrut mount and bearing assembly 10, the hub 28 is preferably formed ofan assembly of two generally circular cups 32, 34 each having an innerbase wall 32 a, 34 a disposed against the base wall 34 a, 32 a of theother cup 34, 32. The two cups 32, 34 have aligned central openingsproviding a clearance hole 36 for inserting a fastener 8 to attach thefree end 3 a of the shock absorber 3 to the hub cup base walls 32 a, 34a, and thereby to the strut mount 12. Further, the upper cup 32 providesa bore 33 for receiving the head 8 a of the fastener 8 and the lower cup34 provides a bore 35 for receiving a portion of the bumper 5 and acircular bearing surface 39 against which is disposed the upper end 5 aof the bumper 5, such that loading from the bumper 5 is transferred tothe damper 30.

Referring to FIGS. 22-24, in one construction of the strut mount andbearing assembly 10, the hub 28 is formed of a generally circularcylindrical body 38 with a counterbore hole 37 for receiving thefastener 8 to connect the hub 28 with the shock absorber shaft end 3 a.In this construction, the strut mount 12 further includes a generallycircular transfer plate 40 attached to the strut mount body 23 andextending across the lower end of the strut mount body bore 27. Thetransfer plate 40 has a central clearance hole 41, through which extendsa portion of shock absorber shaft 3, and circular bearing surface 42against which the upper end 5 a of the bumper 5 is disposed. As such,axial loading is transferred from the bumper 5 to the strut mount 12.

In yet another construction of the strut mount and bearing assembly 10as shown in FIGS. 25-27, the hub 28 is also formed of a generallycircular cylindrical body 38 with a counterbore hole 37 for receivingthe fastener 8. In this construction, the strut mount 12 includes agenerally circular support plate 44 attached to the strut mount body 23and extending across the lower end of the strut mount body bore 27. Thesupport plate 44 has a central clearance hole 42 for receiving a portionof the shock absorber shaft 3, but does not interact directly with thebumper 5. Instead, the hub portion 50 of the spring seat 16 has acounterbore hole 46 providing a bearing surface 48, against which isdisposed the upper end 5 a of the bumper 5. As such, all loading fromthe bumper 5 is transferred to the spring seat 16 as opposed to thestrut mount 12.

Referring to FIGS. 1-5, 12-18, and 20-27, in most constructions of thestrut mount and bearing assembly 10, the spring seat 16 is preferablygenerally axially symmetrical and includes a generally cylindricalcentral hub portion 50 disposeable within the upper end 4 a of thespring 4 and a generally circular flange portion 52 extending radiallyoutwardly from the hub portion 50. The hub portion 50 has an innercircumferential surface 51 defining a central bore 53 and in mostconstructions, includes a generally annular engagement lip 54 extendingradially inwardly from the bore inner surface 51, as shown in FIGS. 2-5,13, 16-18 and 21-24. The flange portion 52 has a first radial surface 56providing the spring contact surface 17 and an opposing, second radialsurface 58 configured to support the attached second bearing race 18,specifically on a bearing radial support surface section 59, asdescribed in further detail below.

Preferably, the spring seat 16 further includes a generally annularshoulder 60 projecting generally axially from the second radial surface58 on the spring seat upper end 16 a. The annular shoulder 60 provideseither an inner circumferential, bearing axial support surface section62 when the second bearing race 18 is diametrically larger than thefirst bearing race 14 (FIGS. 1-13 and 16-27) or an outercircumferential, bearing axial support surface section 64 when thesecond bearing race 18 is diametrically smaller than the first race 14,as shown in FIGS. 14 and 15. In either construction, the bearing secondrace 18 is preferably disposed against and attached to the shouldersupport surface 62 or 64.

In one alternative construction depicted in FIGS. 14 and 15, the springseat 16 is formed with an annular lip 61 extending radially outwardlyfrom the outer perimeter of the flange portion 52. In anotheralternative construction shown in FIGS. 25-27, the hub portion 50 isformed without an inner annular lip and instead the spring seat 16includes an annular lip 63 extending radially outwardly from theshoulder 60. In each alternative construction, the outer annular lip 61or 63 is engageable with a retainer lip 94 or 96, respectively, of thestrut mount 12, as described in detail below. As described in detailbelow, each of the lips 54, 61 or 63 enables assembly of the spring seat16 and the second race 18 onto the strut mount 12 and the first race 14,and after the initial assembly, the lip 54, 61 or 63 retains theassembled components of the strut mount and bearing assembly 10 andprevents disassembly thereof without damaging the components.

Referring to FIGS. 28 and 29, in another alternative construction, thespring seat 16 is asymmetrical about a seat centerline L_(SS) and isconfigured to engage with a spring 4 having a load centerline L_(S) thatis angled or skewed with respect to the shock absorber axis A_(S) andalso supports a second bearing race 18 that is centered about the shockabsorber axis A_(S) (and thus also the strut mount bore centerlineL_(B)). The spring seat 16 includes a generally cylindrical central hubportion 150 and a generally circular, generally wedge-shaped flangeportion 152 extending radially outwardly from the hub portion 150. Thehub portion 150 is disposeable within the upper end 4 a of the spring 4and has a generally circular lower end 150 a and a generally ellipticalupper end 150 b that is angled with respect to the centerline L_(SS)between an axially longest point P_(L) and an axially shortest pointP_(S). The hub portion 150 also has upper and lower innercircumferential surfaces 151, 153, respectively, separated by a radiallyinwardly-extending shoulder 154 defining a central bore 155 andproviding a bumper engagement surface 157. Also, a generally annularengagement lip 154 extends radially inwardly from the upper innersurface 151 of the hub portion 150.

Further, the wedge-shaped flange portion 152 has an axial length orthickness to that varies from a least value at the hub longest pointP_(L) and a greatest value at the hub shortest point P_(S). The flangeportion 152 also has a first radial surface 156 providing the springcontact surface 17, which is angled with respect to the spring seatcenterline L_(SS) and generally coaxial with the spring centerlineL_(S), and an opposing, second radial surface 158 configured to supportthe attached second bearing race 18, which is generally centered aboutthe spring seat centerline L_(SS). Furthermore, the spring seat 16 ofFIGS. 28 and 29 also includes a generally annular shoulder 160projecting generally axially from the second radial surface 158 on thespring seat upper end 16 a. The annular shoulder 160 has an innercircumferential support surface section 162 providing the lower racesurface 26, the bearing second race 18 being preferably disposed againstand attached to the shoulder support surface 162.

In certain constructions as shown in FIGS. 2-5, 12, 13, 16-18 and 22-24,the spring seat 16 is of two-piece construction and includes an upper,inner member 66 formed of a rigid polymeric material (e.g., Peek, nylon,Delrin, etc., filled or not with glass fibers, glass balls, etc.) and alower, outer member 68 formed of an elastomeric material (e.g., naturalor synthetic rubber, filled or not with carbon black, thermoplasticelastomer, polymeric foam, etc.). The upper member 66 provides theshoulder 60, the bearing support surface 62 or 66 and the hub portion 50and the lower member 68 provides the spring contact surface 17. With thepreferred structure and materials, the upper member 66 is sufficientlyrigid to adequately support the second bearing race 18 while the lowermember 68 is capable of at least reducing vibrations within the strutspring 4. Alternatively, the lower member 68 may be formed of a rigidmaterial, such as for example a metallic material (e.g., low carbonsteel), as depicted in FIGS. 14 and 15. In other constructions, thespring seat 16 may alternatively be formed of one piece as shown inFIGS. 21, 25-27, preferably of a rigid polymer, or may be formed ofthree or more pieces, or/and formed of any other appropriate materials.In the construction of FIGS. 28 and 29, the spring seat 16 preferablyincludes an upper, generally annular rigid internal support member 166and a lower, generally annular rigid internal support member 167, eachpreferably formed of a metallic material, and an over-molded body 168preferably formed of a rigid polymeric material.

Referring now to FIGS. 2-5, 11, 14-18, 21-24, 28 and 29, in several ofthe various constructions of the strut mount and bearing assembly 10,the strut mount body 22 includes an inner metallic plate 70 and outerpolymeric body 72 molded onto the plate 70. The inner plate 70 has acentral, generally circular tubular portion 74 defining the strut mountbody bore 25 and a generally circular flange portion 76 extendingradially outwardly from the central tubular portion 74. The outerpolymeric body 72 is either generally wedge-shaped (FIGS. 2-5, 11, 14and 15) or generally circular cylindrical (FIGS. 14-18, 21-24, 28 and29) and provides the bearing support surface 24 and other strut mountbody integral structural features, as described below. Alternatively, asdepicted in FIGS. 25-27, the strut mount body 22 may be of one-piececonstruction, such as for example, formed of a molded polymeric material(as depicted) or cast, sintered, forged and/or machined (or otherwisefabricated) from a metallic material, such as for example, aluminum orstainless steel.

As shown in FIGS. 2-5, 16-18, and 21-29, in most of the constructions ofthe strut mount and bearing assembly 10 described and depicted herein,the second bearing race 18 is sized diametrically larger than the firstbearing race 14, as discussed above. With these structures, the strutmount body 22 is preferably formed such that the upper bearing surface24 has an outer circumferential, race surface axial section 78 generallycentered on either the bearing axis A_(B) or the bore centerline L_(B)and extending generally axially from a race surface radial section 79 ofthe race surface 24. In either case, the axial support surface section78 and the support surface radial section 79 are preferably formed onthe outer polymeric body 72. Further, with the preferred upper racesurface 24, the first bearing race 14 is partially disposed against themount body axial surface section 78 and the spring seat shoulder 60 or160 is disposed circumferentially about the strut mount axial surface78. As such, the outer circumferential, axial surface section 78 of thestrut mount 12 and the inner circumferential, axial support surface 62or 162 of the spring seat 16 enable the bearing assembly 11 to supportradial loading, in addition to the axial thrust load support provided bythe surface radial sections 59 and 79.

Alternatively, as shown in FIGS. 14 and 15, when the first bearing race14 is sized diametrically larger than the second bearing race 18, thestrut mount body 22 preferably further includes an angled, outer annularwall portion 80 extending axially downwardly from a remainder of thebody 22 and circumferentially about the bearing axis A_(B). The outerannular wall portion 80 is spaced radially outwardly from a centralportion 84 of the body 22 so as to define generally annular groove 86,which is sized to receive the annular shoulder 60 of the spring seat 16.The angled race surface 24 is formed adjacent to the inner end of theouter wall portion 80 and an inner circumferential, surface axialsection 88 is provided on the wall inner surface and extending axiallyfrom a surface radial section 89 of the race surface 24, which extendscircumferentially about the outer circumferential bearing supportsurface 64 on the spring seat 16. With this structure, the innercircumferential, support axial surface section 88 of the strut mount 12and the outer circumferential, axial support surface 64 of the springseat 16 enable this variation of the bearing assembly 11 to supportradial loading.

Referring now to FIGS. 2-5, 11, 16-18, 21-24, 28 and 29, in severalconstructions of the mount and bearing assembly 10, the strut mount 12also includes a generally circular retainer lip 90 engageable with thespring seat lip 54 or 154 to retain the spring seat 16 movably coupledwith the strut mount 12. The strut mount retainer lip 90 is eithergenerally coaxial with the bearing axis A_(B) so as to be angled withrespect to the strut mount bore centerline L_(B) (FIGS. 2-5 and 11) orcoaxial with the strut mount bore centerline L_(B) (FIGS. 16-18, 21-24,28 and 29), as discussed in greater detail below.

In “angled” assemblies of the strut mount 12 as disclosed in FIGS. 2-15,11, 14 and 15, the strut mount body 22 further includes a generallytubular wall portion 92 disposed within the spring seat bore 33 andproviding the retainer lip 90. The tubular wall portion 92 extendscircumferentially about the strut mount central bore 12 and axially froma remainder of the strut mount body 22. Further, the tubular wall 92 hasa first, generally circular end 92 a integrally formed with a remainderof the strut mount body 22, preferably the outer polymeric body 52, anda second, free end 92 b. The wall free end 92 b is generally ellipticaland is angled with respect to the bore centerline L_(B), such that thewall 92 has an axially shortest portion W_(S) and an axially longestportion W_(L) spaced about one hundred eighty degrees (180°) from theaxially shortest portion W_(S), as indicated in FIG. 11. The wallportions W_(S), W_(L) are arranged such that each is generally radiallyaligned with a separate one of the most proximal and most distal axialpositions P_(P), P_(D) of the strut mount bearing support surface 24.Further, the strut mount retainer lip 90 extends generally radiallyoutwardly from the tubular wall 92 generally adjacent to the wall secondaxial end 92 b.

In the symmetrical constructions depicted in FIGS. 16-18, 21-24, 28 and29, the strut mount body 22 includes a generally circular cylindricalwall portion 93 disposed within the spring seat bore 53 and providingthe retainer lip 90. The cylindrical wall portion 93 extendscircumferentially about the strut mount central bore 13 and axially froma remainder of the strut mount body 23, and has a generally constantaxial length. The wall 93 has a first, generally circular end 93 aintegrally formed with a remainder of the strut mount body 22,preferably the outer polymeric body 72, and a second, generally circularfree end 93 b. Further, the strut mount retainer lip 90 extendsgenerally radially outwardly from the cylindrical wall portion 93generally adjacent to the wall second axial end 93 b.

With either of the above-structures, the spring seat 16 is rotatablycoupled with the strut mount 12 by inserting the free end 92 b or 93 bof the wall portion 92, 93 respectively, into the spring seat bore 53until the strut mount retainer lip 90 displaces axially past the springseat engagement lip 54. At that point, the interaction between the twolips 54, 92 generally prevents axial displacement of the spring seat 16with respect to the strut mount 12 under normal operating conditions,but enables the spring seat 16 to angularly displace about the strutmount tubular wall portion 92 or 93. When the orientation of the strutmount retainer lip 90 is angled with respect to the strut borecenterline L_(B), but coaxial about the spring centerline L_(S), theaxially symmetrical spring seat 16 is positioned generally centeredabout the coaxial bearing axis A_(B) and spring centerline L_(S).Further, when the orientation of the strut mount retainer lip 90 iscoaxial with respect to the strut bore centerline L_(B), the axiallysymmetrical spring seat 16 is positioned generally centered about thecoaxial strut mount bore centerline L_(B) and the shock absorber shaftaxis A_(S).

In the alternative construction depicted in FIGS. 14 and 15, the angledouter wall portion 80 includes a generally circular retainer lip 94extending radially inwardly from adjacent to the wall outer end 80 a,and is generally coaxial with the spring centerline L_(S). The strutmount retainer lip 94 is engageable with the spring seat outer annularengagement lip 61 to retain the spring seat 16 movably coupled with thestrut mount 12, such that the spring seat 16 is angularly displaceableabout the spring centerline L_(S). In the construction depicted in FIGS.25-27, the strut mount body 23 further includes an outer, generallycircular tubular wall portion 95 extending generally axially from aremainder of the body 23. The tubular wall portion 95 includes agenerally circular retainer lip 96 extending radially inwardly fromadjacent to the wall outer end 95 a, and is generally coaxial with thestrut mount bore centerline L_(B). The strut mount retainer lip 96 isengageable with the spring seat outer annular lip 63 to retain thespring seat 16 movably coupled with the strut mount 12, such that thespring seat 16 is angularly displaceable about the generally coaxialstrut mount bore centerline L_(B) and shock absorber shaft axis A_(S).

Further, to prevent ingress of contaminants into the bearing assembly11, the strut mount 12 preferably further includes a generally circularskirt 91 extending generally circumferentially about the bearing axisA_(B), so as to be angled with respect to the bore centerline L_(B)(FIGS. 1-15) or generally coaxial with bore centerline L_(B) (FIGS.16-29). The skirt 91 is disposed circumferentially about the secondbearing race 18 of the spring seat 16, most preferably about the springseat shoulder 60, so as to provide a barrier about the bearing races 14,18. Furthermore, most constructions of the strut mount and bearingassembly 10 preferably further includes inner and outer annular seals97, 98, respectively, disposed on either side of the bearing assembly11. Specifically, in the constructions depicted in FIGS. 1-13 and 16-21,the inner seal 97 is mounted on the inner end 50 a of the spring seathub portion 50 and engages with an outer circumferential surface 99 ofthe strut mount body 22, whereas the outer seal 98 is mounted on theouter perimeter of the spring seat shoulder 60 and engages with an innercircumferential surface 91 a of the tubular skirt 91. Most preferably,the seals 97, 98 are generally formed as disclosed in U.S. PatentApplication Publication No. US 2013/0277161A1, published on Oct. 24,2013, the entire contents of which are incorporated by reference herein.Furthermore, in the construction depicted in FIGS. 14 and 15, the innerseal 97 is mounted on the shoulder 60 of the spring seat 16 and engageswith an outer circumferential surface 100 of the strut mount body 22 andthe outer seal 98 is mounted on the outer perimeter of the spring seatflange portion 52 and engages with the inner surface 91 a of the tubularskirt 91. Furthermore, the construction depicted in FIGS. 25-27 does notinclude the inner and outer seals.

Due to the following structural features of the strut mount and bearingassembly 10, the axial space requirements, or total axial length D_(AO)of the assembly 10, is minimized. First, by having the upper race 14attached (or formed) directly on the strut mount 12 and the lower race18 attached/formed directly on the spring seat 16, instead of requiringadditional components to attach the upper race 14 to the mount 12 andthe lower race 18 to the seat 16 as per the current state of the art,and having the spring seat 16 directly coupled with the strut mount 12,all components for a separate bearing assembly attached individually tothe strut mount 12 and to the spring seat 16 are eliminated. Also, bypositioning the upper race 24 and the spring contact surface 17 inrelatively close proximity to the upper attachment surface 15, asindicated by the above-discussed first and second ratios R₁, R₂,minimizes the required axial height D_(AO) of the strut mount andbearing assembly 10. Further, the arrangement of the hub 28 and damper30 being coaxially disposed within the strut mount 12, and the bearingraces 14, 18 being disposed about the hub 28 and damper 30, reduces theaxial stacking of such components as found in previously known strutmount assemblies, and by having a single unit mount-damper-hub asopposed to two or more distinct components facilitates handling of thesecomponents during the assembly of the strut mount and bearing assembly10 into the vehicle suspension. Additionally, having the upper race 14mounted on the strut mount 12 to form a single unit eliminates thepotential for relative movement between the upper race and the mount aswith previously known strut bearing assemblies, and thereby eliminatesthe noise generated by such relative motion as found with prior artstrut bearing assemblies.

Also, by forming the bearing races 14, 18 such that the lower race 18 isdisposed circumferentially about the upper race 14, and the uppermostportion of upper race 14 being located as proximal to the strut mountupper end 12 a as reasonably practicable, it is possible to provide abearing assembly 11 that is angled, so as to be aligned with the springcenterline L_(S), while minimizing axial length/height D_(AO). Due tominimization of the overall axial height HA of the strut mount assembly10, the additional space may be utilized to increase the length of thesuspension spring 4, which increases vehicle riding comfort, to reducethe vehicle hood height, and/or to provide more space between the strutmount 12 and the vehicle hood (not shown) for better pedestrianprotection and more flexibility for the front vehicle design.

It will be appreciated by those skilled in the art that changes could bemade to the embodiments described above without departing from the broadinventive concept thereof. It is understood, therefore, that thisinvention is not limited to the particular embodiments disclosed, but itis intended to cover modifications within the spirit and scope of thepresent invention as generally defined in the appended claims.

1-20. (canceled)
 21. A strut mount and bearing assembly for connecting awheel strut unit with a vehicle body, the strut unit including a shockabsorber with a shaft extending along a central shock absorber axis anda suspension spring having a load centerline, the assembly comprising: astrut mount including a body formed of a substantially rigid material ora combination of rigid materials and having upper and lower ends, acentral bore extending generally between the upper and lower ends and agenerally annular upper race surface disposed between the upper andlower ends and extending circumferentially about the bore, the mountupper end being configured to fixedly connect with the vehicle body andhaving a generally flat attachment surface extending substantiallyperpendicularly to the centerline and disposeable against a surface ofthe vehicle body, the central bore being configured to receive an upperend of the shock absorber shaft and having a centerline extendinggenerally collinearly with the shock absorber axis; a generally annular,first bearing race disposed on or provided by the upper race surface ofthe strut mount such that the first bearing race is substantiallyimmovable with respect to the vehicle body, the first bearing racehaving a central axis generally coaxial or parallel with the spring loadcenterline; a spring seat movably coupled with the strut mount andhaving an upper end with a generally annular lower race surface and alower end with a generally circular engagement surface contactable by anupper end of the suspension spring, the engagement surface having acenter and a diameter; a generally annular, second bearing race disposedon or provided by the lower race surface of the spring seat and arrangedfacing generally toward and spaced axially from the first bearing race;and a plurality of rolling elements disposed between the first andsecond bearing races so as to form a bearing; wherein the strut mountand the spring seat are sized and configured such that a ratio of thediameter of the spring engagement surface to an axial distance betweenthe upper attachment surface and the engagement surface center isgreater than two (2).
 22. The strut mount and bearing assembly asrecited in claim 21 wherein: the strut mount body has an innercircumferential surface defining a body bore; and the strut mountfurther includes a hub disposed within the body bore, the hub providingthe strut mount central bore and being configured to connect with theshock absorber upper end, and a generally circular cylindrical damperdisposed generally coaxially between and connecting the hub with thestrut mount body, the damper being formed of an elastomeric material andconfigured to reduce vibration within the strut mount and bearingassembly.
 23. The strut mount and bearing assembly as recited in claim22 wherein the damper has an inside diameter, the hub has an outsidediameter sized larger than the damper inside diameter when separate fromthe strut mount and bearing assembly such that damper is compressedbetween the hub and the strut mount body so as to provide a compressivepreload on the damper.
 24. The strut mount and bearing assembly asrecited in claim 22 wherein: the strut mount is formed of a rigidpolymeric material or a combination of a rigid polymeric material and ametallic material; and the hub is formed of a metallic material.
 25. Thestrut mount and bearing assembly as recited in claim 21 wherein thebearing has a pitch diameter and the first race surface is formed on thestrut mount such that a ratio of the bearing pitch diameter to an axialdistance between the center of the pitch diameter and the strut mountattachment surface is greater than three (3).
 26. The strut mount andbearing assembly as recited in claim 25 wherein: the strut mount and thespring seat are sized and configured such that the ratio of the diameterof the spring engagement surface to the axial distance between the upperattachment surface and the engagement surface center is greater thanthree (3); and the first race surface is formed on the strut mount suchthat the ratio of the bearing pitch diameter to the axial distancebetween the center of the pitch diameter and the strut mount attachmentsurface is greater than five (5).
 27. The strut mount and bearingassembly as recited in claim 21 wherein one of: the second bearing racehas a diameter larger than a diameter of the first bearing race and isdisposed at least partially circumferentially about the first bearingrace; and the first bearing race has a diameter larger than a diameterof the second bearing race and is disposed at least partiallycircumferentially about the second bearing race.
 28. The strut mount andbearing assembly as recited in claim 21 wherein the strut mount includesa generally cylindrical central section providing the strut mount lowerend and a generally annular flange section extending radially outwardlyfrom the central section and providing the strut mount upper end and theupper attachment surface, the first race surface being formed on thecylindrical section and having at least a portion located generallyadjacent to the flange section.
 29. The strut mount and bearing assemblyas recited in claim 28 wherein the strut mount flange section includes aplurality of through holes each configured to receive a separatefastener engageable with the vehicle body to fixedly connect the strutmount to the vehicle body.
 30. The strut mount assembly as recited inclaim 28 wherein: the first race surface is formed on the strut mountsuch that the bearing central axis is skewed with respect to the borecenterline so as to define an angle with a value greater than zerodegrees and the spring seat is coupled with the strut mount so as to beangularly displaceable about the bearing axis; and the strut mountincludes a generally wedge-shaped, circular cylindrical body having agenerally circular, angled support surface proximal to the strut mountlower end and extending circumferentially about the first bearing raceaxis, the support surface having a most proximal axial position withrespect to the strut mount upper end and a most distal axial positionwith respect to the strut mount upper end, the first bearing race beingdisposed on the support surface.
 31. The strut mount and bearingassembly as recited in claim 29 wherein the strut mount cylindrical bodyincludes an inner metallic plate, the plate having a central tubularportion and generally circular flange portion extending radiallyoutwardly from the central tubular portion, and an outer, generallywedge-shaped cylindrical polymeric body molded onto the metallic plate.32. The strut mount and bearing assembly as recited in claim 21 whereinthe spring seat includes a central bore and a generally annular lipextending radially inwardly from the bore and the strut mount includes agenerally circular retainer lip engageable with the spring seat lip toretain the spring seat coupled with the strut mount, the strut mountretainer lip being generally coaxial with the first bearing race so asto be angled with respect to the strut mount bore centerline; and 33.The strut mount and bearing assembly as recited in claim 32 wherein thestrut mount further includes a generally tubular wall extendingcircumferentially about the strut mount central bore, disposed withinthe spring seat bore and having a first, generally circular endintegrally formed with a remainder of the strut mount body and a second,generally elliptical free end angled with respect to the strut mountbore centerline such that the tubular wall has an axially shortestportion and an axially longest portion spaced about one hundred eightydegrees from the axially shortest portion, the strut mount retainer lipextending radially outwardly from the tubular wall generally adjacent tothe wall second axial end.
 34. The strut mount and bearing assembly asrecited in claim 33 wherein the strut mount includes a generallycircular skirt extending generally circumferentially about the bearingcentral axis so as to be angled with respect to the strut mount borecenterline and disposeable circumferentially about the second bearingrace of the spring seat so as to prevent ingress of materials into thefirst and second bearing races.
 35. The strut mount and bearing assemblyas recited in claim 21 wherein the spring seat includes a generallycylindrical central hub portion disposeable within the upper end of thespring and a flange portion extending radially from the hub portion, theflange having a first radial surface providing the spring contactsurface and an opposing, second radial surface providing the second racesurface.
 36. The strut mount and bearing assembly as recited in claim 35wherein the spring seat includes an upper member formed of asubstantially rigid polymer and including the central hub portion andthe flange first radial surface and a lower member formed of asubstantially flexible elastomeric material, attached to the uppermember and providing the flange second, lower surface.
 37. The strutmount and bearing assembly as recited in claim 36 wherein the springseat includes a generally annular shoulder projecting generally axiallyfrom the spring seat upper end and providing one of an innercircumferential support surface and an outer circumferential supportsurface, the second race surface being at least partially disposed onthe shoulder support surface.
 38. The strut mount and bearing assemblyas recited in claim 37 wherein one of: the strut mount first racesurface is an outer circumferential surface generally centered on thespring axis and the spring seat shoulder is disposed circumferentiallyabout the strut mount first race surface; and the strut mount racesurface includes an inner circumferential surface generally centered onthe spring axis and the spring seat shoulder is disposed within thestrut mount support surface.